Elastic-fluid turbine.



. A. WIBERG.

ELASTC FLUID TURBINE.

' APPLICATION FILED MAY|6,\9|1. 1,257,167, Patented Feb. 19, 1918.

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OSCAR ANTON WIBERG, OF FINSPONG, SWEDEN, ASSIGNOB T AKTIBOLAGET IJUNGSTRMS ANGTURBIN, 0F STOCKHOLM, SWEDEN.

ELAs'rIc-FLUID ,'rUaBINE.

Specicatiouof Letters Patent. Patented Feb. 19, 1918.

Applicationled May 16, 1917. Serial No. 169,105.

To all whom t may concern.'

Be it known that I, OSCAR ANTON WIBERG,

A a subject of the King o f,l Sweden, residing through another system.

Turbines of this character are very efective for the purpose intended, but have the limitation that the output cannot be distributed arbitrarily between the rotor shafts because the effect of the motive fluid on the blades is to impart equal, or' substantially' equal, turning moments to the rotors and their shafts.

When such .turbines drive electric generators, it is desirable to have one of the rotor shafts drive |an exciter, lubricating pump, or other load, in additionto its mainzgigenerator, thereby requiring a greater output from one shaft than from the other. the case of turbo-alternators, this is now accomplished by connecting the two generators in parallel so that the rotors are compelled to move in synchronism.- Under these conditions the turbine rotor which drives the additional load tends to lag behind the other,

and hence A current Hows to its generator from the other in suiicient amount to prevent it from dropping out of step. The ob jection to this is that one generator always carries a greaterload than the other which may at times be a very substantial amount. My invention has for its object to avoid this unequal loading .of the generators and to provide means whereby, in a turbine of the character described, the blade carrying rotors can be made to develop unequal amounts of work and hence to drive unequal loads.

In the accompanying drawing, which is illustrative of my invention, Figure 1 is a partial axiaLsection of one embodiment'of my invention; Fig. 2 is a similar section of a modification, and Fig. 3 is a diagrammatic view of a turbo-generator set. y i

Referring first to Fig. 3, 4 and 5 indlcate bine rotors which revolve in opposite directions and are provided with a system of blades comprising concentric rings of blades through which the motive fluid flows radially outward, and a system of blades through which the motive Huid exhausting from the radial system Hows in an axial direction.

.6 and 7 indicate the main generators which are driven by the rotors, and v8 indicates an exciter or other additional load which is driven by one of the rotors, as 5 for example. The main generators may be connected in parallel as usual to insure lthe same shaft speed for both rotors.

Referring to Fig. 1, 4 and 5 indicate the rotors. Mounted on the rotor 4 are concentric rings of blades 9 coperating with rings of blades 10 on the rotor 5. These'rotors may be provided with as many concentric rings of blades as is desired. Each rotor'is provided with an enlarged rim 11 in which are mounted the blades 12, the latter being of any suitable type. Coperating with these blades are statlonary directing devices or bladesl which are carried by the ring 14 which also forms a means for delecting the exhaust steam from the radial flow system through the axial flow system. The ring is carried by projections 15 that are secured to the inclosing casing which has been omitted for simplicity, but which is of ordinary construction. The inner ends of the directing device 13 are secured to rings 16 whose inner surfaces stand in close roximity to projections on the rotor 5 to re uce leakage.V

In a turbine constructed as described, the two rotors have equal, or substantially equal, turning moments. As above explalned, it is sometimes desirable to have one rotor do more work than the other. complished in a number of ways. For example, by regulating the amount of steam which flows through one set of axial iiow blades, by changing the angles of one set of said blades, by changing` the lengths of one set of said blades, or by using a different diameter for one set than the other vaccompanied by a difference in amount of Huid which can flow per` unit of time.

In Fig. 1 is shown an arrangement whereby the amount of steam flowing through one part of the axial {iow system 'can be controlled, the parts of the System being alike. To this end the right-hand'ring 16 is enlarged to form a seat for the ringor gridiron valve 18, the latter coperating with a xed This can be acto the blades on the discharge side. To permit the valve to be adjusted the ringy 14 is slotted at its upper end to receive a projection 20 on the valve. The periphery'of the projection is provided with gear teeth which mesh with the teeth of the worm 21.'

On the end of the worm shaft and outside 'of the casing is a hand wheel 22, by means of which the valve canbe adjusted to regulate the flow of steam.

In some cases it is sufficient to fix the outputs of the two rotors once for all. To this end one Set of axial flow blades is made shorter than the other, as shown in Fig. 2, so that a greater amount of steam will How through one side than the other, and hence one 'rotor will have a greater-turning moment for a given flow of steam than the other. Thisarrangement is-somewhat simpler than the one shown in Fig. 2, and is satisfactory for many purposes.

Referring to the drawing, 12 and 13 indicate the rotating and stationary blades respectively for one-half of the axial flow system, and 23 and 24 the stationary and 1 '0- tating blades of the other half of the axial flow system. It will be noted that the blades 23 and 24 4are substantially shorter than blades 12 and 13, and hence less steam will flow through them than through the blades 12 and 13.

In accordance with the provisions of the patent statutes, I have described the principle of operation of my invention, together with the apparatus which I now consider to represent the best embodiment thereof, but I desire to have it understood that the aparatus shown 1s only illustrative, and t at the invention can be carried out by otherA means. v.

What I clalm as new and desire to secure by Letters Patent of the United States, is

directions and have radial and axial flow blade systems, and means for causing the rotors to deliver unequal amounts of power.

3. In an elastic Huid turbine, the combination of rotors. which revolve in opposite directionsv and have radial and axial ilow blade systems, with means acting on the ax'- vial iiow blade system for causing the rotors and a second System which assists the rst and comprises moving blades and stationary directing devices, the blades in the second system for a given iiow of motive Huid being arranged to exert unequal torque on said rotors.

5. In an elastic fluid turbine, the combination of rotors which revolve in opposite directions and have a radial flow blade system between them, and an axial flow blade system comprising` stationary fluid directing devices and rows of blades which are mounted lon the peripheries of the rotors, the said devicesand blades of one part of the system being longer than those of the other to cause the rotors to deliver unequal power.

6. In an elastic Huid turbine, the combination of a pair of rotors which revolve in opposite directions and have a radial outflow blade system between them and also an axial flow blade system comprising stal tem comprising concentric rings of blades,

tionary directing devices and blades which to flow through one portion of the axial i flow system than through the other.

7. The combination in an elastic iiuidturbine comprising a pair of rotors which revolve in opposlte dlrections and have a radial flow system between them, and separate axial flow systems which receive the exhaust 'from the radial flow system in parallel. said rotors beingy connected to unequal loads, of

means for dividing the elastic fluid betweenv said axial ilow systems in accordance with said unequal loads.

In testlmony whereof I aliix my signature in presence of two witnesses.

. OSCAR ANTON WIBERG.' Witnesses:

Ttmo ALUNCY, GUNNAR'BABNS. 

